US20130121812A1 - Wet Gas Compression Systems with a Thermoacoustic Resonator - Google Patents
Wet Gas Compression Systems with a Thermoacoustic Resonator Download PDFInfo
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- US20130121812A1 US20130121812A1 US13/295,208 US201113295208A US2013121812A1 US 20130121812 A1 US20130121812 A1 US 20130121812A1 US 201113295208 A US201113295208 A US 201113295208A US 2013121812 A1 US2013121812 A1 US 2013121812A1
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- wet gas
- compression system
- gas compression
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- 239000007791 liquid phase Substances 0.000 claims description 5
- 239000002918 waste heat Substances 0.000 claims description 4
- 239000003345 natural gas Substances 0.000 claims description 3
- 230000003628 erosive effect Effects 0.000 description 9
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D31/00—Pumping liquids and elastic fluids at the same time
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/0318—Processes
- Y10T137/0391—Affecting flow by the addition of material or energy
Definitions
- the present application and the resultant patent relate generally to wet gas compression systems and more particularly relate to a wet gas compression system using a thermoacoustic resonator to break up water droplets in a gas stream before reaching a compressor.
- Natural gas and other types of fuels may include a liquid component therein.
- Such “wet” gases may have a significant liquid volume.
- liquid droplets in such wet gases may cause erosion or embrittlement of the impellers or other components.
- rotor unbalance may result from such erosion.
- the negative interaction between the liquid droplets and the compressor surfaces, such as the impellers, end walls, seals, and the like, may be significant. Erosion is known to be a function essentially of a combination of the relative velocity of the droplets during impact, droplet mass size, and impact angle. Erosion may lead to performance degradation, reduced compressor and component lifetime, and an overall increase in maintenance requirements.
- Such systems and methods may minimize the impact of erosion and other damage caused by large liquid droplets in a wet gas flow while avoiding or at least reducing the need for liquid-gas separators, supersonic shocks, and the like.
- the present application and the resultant patent thus provide a wet gas compression system for a wet gas flow having a number of liquid droplets therein.
- the wet gas compression system may include a pipe, a compressor in communication with the pipe, and a thermoacoustic resonator in communication with the pipe so as to break up the liquid droplets in the wet gas flow.
- the present application and the resultant patent further provide a method of breaking up a number of large liquid droplets in a wet gas flow upstream of a compressor.
- the method may include the steps of flowing the wet gas flow through a pipe, creating a number of acoustic waves about the wet gas flow with a thermoacoustic resonator, reducing a relative velocity of a gaseous phase to a liquid phase of the wet gas flow, and overcoming a surface tension of the number of large liquid droplets to break the large liquid droplets into a number of small liquid droplets.
- Other methods also may be described herein.
- the present application and the resultant patent further provide a wet gas compression system for a wet gas flow having a number of liquid droplets therein.
- the wet gas compression system may include a pipe, a compressor in communication with the pipe, and a thermoacoustic resonator in communication with the pipe and positioned upstream of the compressor.
- the thermoacoustic resonator may include a hot heat exchanger, a cold heat exchanger, and a regenerator therebetween so as to produce a number of acoustic waves into the wet gas flow.
- Other systems also may be described herein.
- FIG. 1 is a schematic diagram of a known wet gas compressor with a portion of a pipe section.
- FIG. 2 is a schematic diagram of an example of a wet gas compression system as may be described herein with a thermoacoustic resonator.
- FIG. 3 is a schematic diagram of the thermoacoustic resonator of the wet gas compression system of FIG. 2 .
- FIG. 4 is a chart showing the relative velocity of the liquid and the gaseous phases of the wet gas flow about the thermoacoustic resonator of the wet gas compression system of FIG. 2 .
- FIG. 5 is a partial side view of an example of an alternative embodiment of a wet gas compression system with a thermoacoustic resonator as may be described herein.
- FIG. 6 is a partial side view of an example of an alternative embodiment of a wet gas compression system with a thermoacoustic resonator as may be described herein.
- FIG. 7 is a partial side view of an example of an alternative embodiment of a wet gas compression system with a thermoacoustic resonator as may be described herein.
- FIG. 1 shows an example of a known wet gas compressor 10 .
- the wet gas compressor 10 may be of conventional design and may include a number of stages with a number of impellers 20 positioned on a shaft 30 for rotation therewith among a number of stators.
- the wet gas compressor 10 also may include an inlet section 40 .
- the inlet section 40 may be an inlet scroll 50 and the like positioned about the impellers 20 .
- Other types and configurations of wet gas compressors 10 may be known.
- a pipe section 60 may be in communication with the inlet section 40 of the wet gas compressor 10 .
- the pipe section 60 may be of any desired size, shape, or length. Any number of pipe sections 60 may be used herein and may be joined in a conventional manner.
- FIG. 2 shows an example of a wet gas compression system 100 as may be described herein.
- the wet gas compression system 100 may include a compressor 110 positioned about a pipe 120 .
- the compressor 110 may be similar to the compressor 10 described above. Any type or number of compressors 110 may be used herein.
- the pipe 120 may have any size, shape, length, or any number of sections.
- the pipe 120 may be in communication with a well head 130 .
- a wet gas flow 140 comes out of the well head 130 and flows through the compressor 110 and then further downstream.
- the wet gas flow 140 may include gaseous phase 145 as well as a number of large liquid droplets 150 in a liquid phase 155 .
- the wet gas flow 140 may be a natural gas, other types of fuels, and the like. Other components and other configurations also may be used herein.
- the wet gas compression system 100 also may include a thermoacoustic resonator 160 .
- the thermoacoustic resonator 160 uses an internal temperature differential to induce high amplitude acoustic waves in an efficient manner.
- the thermoacoustic resonator 160 may be coupled to the pipe 120 downstream of the well head 130 and upstream of the compressor 110 . Any number of thermoacoustic resonators 160 may be used herein.
- the thermoacoustic resonator 160 may include acoustic chamber 170 .
- the acoustic chamber 170 may be in direct communication with the pipe 120 such that the wet gas flow 140 floods the acoustic chamber 170 .
- the acoustic chamber 170 may have any size, shape, or configuration.
- the thermoacoustic resonator 160 may include a hot heat exchanger 180 , a cold heat exchanger 190 , and a passive heat regenerator 200 positioned therebetween.
- a heat source 210 rejects heat to the wet gas flow 140 thereabout.
- the heat source 210 may include any type of heat and any type of heat source. For example, waste heat from the compressor 110 or elsewhere may be used.
- the cold heat exchanger 190 heat may be accepted from the wet gas 140 and transferred to a cooling stream or a heat sink 220 for disposal or use elsewhere.
- the passive heat regenerator 200 may include a stack of plates 230 and the like. Any type of regenerator with good thermal efficiency may be used herein.
- thermoacoustic waves 240 act as pressure waves that propagate through the acoustic chamber 170 and into the pipe 120 .
- the wavelengths and other characteristics of the acoustic waves 240 may be varied herein.
- Other types of thermoacoustic resonators and other means for producing the acoustic waves 240 also may be used herein.
- Other components and other configurations also may be used herein.
- the pressure front caused by the acoustic waves 240 interacts with the wet gas flow 140 in the pipe 120 .
- the interaction of the acoustic waves 240 may cause a rapid velocity change in the gaseous phase 145 of the wet gas flow 140 .
- the change in the relative velocity between the gaseous phase 145 and the liquid phase 155 of the wet gas flow 140 thus may break up the large liquid droplets 150 into a number of smaller liquid droplets 250 as the wet gas flow 140 passes through the acoustic waves 240 .
- Droplet break up may be largely a function of the relative velocity between the gaseous phase 145 and the liquid phase 155 .
- the potential for droplet break up may be evaluated based upon the Weber number of the wet gas flow 140 .
- the Weber number may be calculated in the context of the wet gas flow 140 herein as follows:
- P g is the density of the fluid (kg/m 3 )
- Y R is the relative velocity (m/s)
- d is the droplet diameter (in)
- ⁇ is the surface tension (n/m).
- the Weber number is a non-dimensional measure of the relative importance of the inertia of the fluid as compared to the droplet surface tension.
- the large liquid droplets 150 thus may be broken down into the smaller liquid droplets 250 if the Weber number indicates that the kinetic energy of the gaseous phase 145 may overcome the surface tension of the droplets 150 .
- Other types of droplet evaluation and other types of protocols may be used herein.
- the energy of the acoustic waves 240 may be partially transferred into droplet break up and partially transferred into dissipation in the wet gas flow 140 .
- Dissipation means a deposition of heat into the wet gas flow 140 . This heat leads largely to liquid evaporation as opposed to a temperature increase and therefore may be beneficial to overall compressor performance.
- the wet gas flow 140 continues towards the compressor inlet section 40 with the smaller liquid droplets 250 therein so as to reduce harmful erosion on the compressor blades 20 and the like.
- the wet gas compression system 100 with the thermoacoustic resonator 160 thus should improve overall lifetime and efficiency of the compressor 110 . Specifically, removal of the large liquid droplets 150 may improve erosion damage while higher compressor efficiency may be achieved due to evaporation. Moreover, because the thermoacoustic resonator 160 uses no moving parts, the thermoacoustic resonator 160 should have a long lifetime with low maintenance requirements. Further, because the thermoacoustic resonator 160 may use waste heat from the compressor 110 or elsewhere, the thermoacoustic resonator 160 may not result in parasitic energy loses. The thermoacoustic resonator 160 also may avoid a pressure drop therethrough such that the main compressor duty may not be increased.
- thermoacoustic resonator 160 also may be positioned elsewhere.
- FIG. 5 and FIG. 6 show the use of the thermoacoustic resonator 160 about a convergent-divergent nozzle 260 or other type of variable cross-section nozzle.
- the convergent-divergent nozzle 260 also is known as a de Laval nozzle and the like, may include a convergent section 270 , a throat section 280 , and a divergent section 290 .
- the convergent-divergent nozzle 260 may reduce the large liquid droplets 150 via a supersonic shock at a shock point 300 .
- thermoacoustic resonator 160 may be positioned on an upstream section of pipe 310 .
- the thermoacoustic resonator 160 may be positioned on a downstream section of pipe 320 .
- the thermoacoustic resonator 160 may be positioned anywhere about or along the convergent-divergent nozzle 260 so as to assist and promote droplet break up in a manner similar to that described above.
- Multiple thermo acoustic resonators 160 may be used herein.
- Other type of pipes and other types of nozzles may be used herein.
- Other components and other configurations also may be used herein.
- thermoacoustic resonator 160 may be physically separated from the wet gas flow 140 in the pipe 120 .
- the thermoacoustic resonator 160 may be connected to the pipe 120 via a moving piston 330 and the like.
- the acoustic waves 240 may drive the moving piston 330 into contact with the pipe 120 such that the waves continue therein via the mechanical contact.
- the use of the piston 330 also allows the use of a different working medium within the thermoacoustic resonator 160 .
- Mediums such as helium, nitrogen, or other gases may be used.
- the use of an alternative medium may be beneficial from an efficiency and stability point of view, i.e., increased efficiency in the conversion of heat to acoustic energy.
- Other types of mechanical systems also may be used herein.
Abstract
Description
- The present application and the resultant patent relate generally to wet gas compression systems and more particularly relate to a wet gas compression system using a thermoacoustic resonator to break up water droplets in a gas stream before reaching a compressor.
- Natural gas and other types of fuels may include a liquid component therein. Such “wet” gases may have a significant liquid volume. In conventional compressors, liquid droplets in such wet gases may cause erosion or embrittlement of the impellers or other components. Moreover, rotor unbalance may result from such erosion. Specifically, the negative interaction between the liquid droplets and the compressor surfaces, such as the impellers, end walls, seals, and the like, may be significant. Erosion is known to be a function essentially of a combination of the relative velocity of the droplets during impact, droplet mass size, and impact angle. Erosion may lead to performance degradation, reduced compressor and component lifetime, and an overall increase in maintenance requirements.
- Current wet gas compressors may use an upstream liquid-gas separator to separate the liquid droplets from the gas stream so as to limit or at least localize the impact of erosion and other damage caused by the liquid droplets. The equipment required for separation, however, generally requires additional power consumption. Another approach is to use a convergent-divergent nozzle such as a de Laval nozzle and the like so as to accelerate the gas flow to a supersonic velocity. The resulting supersonic shock may break up the liquid droplets. The supersonic shock, however, also may lead to a pressure drop upstream of the compressor and therefore an increase in overall compressor duty.
- There is thus a desire for improved wet gas compression systems and methods of avoiding erosion. Preferably, such systems and methods may minimize the impact of erosion and other damage caused by large liquid droplets in a wet gas flow while avoiding or at least reducing the need for liquid-gas separators, supersonic shocks, and the like.
- The present application and the resultant patent thus provide a wet gas compression system for a wet gas flow having a number of liquid droplets therein. The wet gas compression system may include a pipe, a compressor in communication with the pipe, and a thermoacoustic resonator in communication with the pipe so as to break up the liquid droplets in the wet gas flow.
- The present application and the resultant patent further provide a method of breaking up a number of large liquid droplets in a wet gas flow upstream of a compressor. The method may include the steps of flowing the wet gas flow through a pipe, creating a number of acoustic waves about the wet gas flow with a thermoacoustic resonator, reducing a relative velocity of a gaseous phase to a liquid phase of the wet gas flow, and overcoming a surface tension of the number of large liquid droplets to break the large liquid droplets into a number of small liquid droplets. Other methods also may be described herein.
- The present application and the resultant patent further provide a wet gas compression system for a wet gas flow having a number of liquid droplets therein. The wet gas compression system may include a pipe, a compressor in communication with the pipe, and a thermoacoustic resonator in communication with the pipe and positioned upstream of the compressor. The thermoacoustic resonator may include a hot heat exchanger, a cold heat exchanger, and a regenerator therebetween so as to produce a number of acoustic waves into the wet gas flow. Other systems also may be described herein.
- These and other features and improvements of the present application and the resultant patent will become apparent to one of ordinary skill in the art upon review of the following detailed description when taken in conjunction with the several drawings and the appended claims.
-
FIG. 1 is a schematic diagram of a known wet gas compressor with a portion of a pipe section. -
FIG. 2 is a schematic diagram of an example of a wet gas compression system as may be described herein with a thermoacoustic resonator. -
FIG. 3 is a schematic diagram of the thermoacoustic resonator of the wet gas compression system ofFIG. 2 . -
FIG. 4 is a chart showing the relative velocity of the liquid and the gaseous phases of the wet gas flow about the thermoacoustic resonator of the wet gas compression system ofFIG. 2 . -
FIG. 5 is a partial side view of an example of an alternative embodiment of a wet gas compression system with a thermoacoustic resonator as may be described herein. -
FIG. 6 is a partial side view of an example of an alternative embodiment of a wet gas compression system with a thermoacoustic resonator as may be described herein. -
FIG. 7 is a partial side view of an example of an alternative embodiment of a wet gas compression system with a thermoacoustic resonator as may be described herein. - Referring now to the drawings, in which like numerals refer to like elements throughout the several views,
FIG. 1 shows an example of a knownwet gas compressor 10. Thewet gas compressor 10 may be of conventional design and may include a number of stages with a number ofimpellers 20 positioned on ashaft 30 for rotation therewith among a number of stators. Thewet gas compressor 10 also may include aninlet section 40. Theinlet section 40 may be aninlet scroll 50 and the like positioned about theimpellers 20. Other types and configurations ofwet gas compressors 10 may be known. Apipe section 60 may be in communication with theinlet section 40 of thewet gas compressor 10. Thepipe section 60 may be of any desired size, shape, or length. Any number ofpipe sections 60 may be used herein and may be joined in a conventional manner. -
FIG. 2 shows an example of a wetgas compression system 100 as may be described herein. The wetgas compression system 100 may include acompressor 110 positioned about apipe 120. Thecompressor 110 may be similar to thecompressor 10 described above. Any type or number ofcompressors 110 may be used herein. Likewise, thepipe 120 may have any size, shape, length, or any number of sections. Thepipe 120 may be in communication with a wellhead 130. Awet gas flow 140 comes out of thewell head 130 and flows through thecompressor 110 and then further downstream. Thewet gas flow 140 may includegaseous phase 145 as well as a number of largeliquid droplets 150 in aliquid phase 155. Thewet gas flow 140 may be a natural gas, other types of fuels, and the like. Other components and other configurations also may be used herein. - The wet
gas compression system 100 also may include athermoacoustic resonator 160. Generally described, thethermoacoustic resonator 160 uses an internal temperature differential to induce high amplitude acoustic waves in an efficient manner. Thethermoacoustic resonator 160 may be coupled to thepipe 120 downstream of thewell head 130 and upstream of thecompressor 110. Any number ofthermoacoustic resonators 160 may be used herein. - The
thermoacoustic resonator 160 may includeacoustic chamber 170. Theacoustic chamber 170 may be in direct communication with thepipe 120 such that thewet gas flow 140 floods theacoustic chamber 170. Subject to the fact that the configuration of theacoustic chamber 170 may have an impact on the nature and the wavelength of the acoustic waves produced therein, theacoustic chamber 170 may have any size, shape, or configuration. - The
thermoacoustic resonator 160 may include ahot heat exchanger 180, acold heat exchanger 190, and apassive heat regenerator 200 positioned therebetween. At thehot heat exchanger 180, aheat source 210 rejects heat to thewet gas flow 140 thereabout. Theheat source 210 may include any type of heat and any type of heat source. For example, waste heat from thecompressor 110 or elsewhere may be used. At thecold heat exchanger 190, heat may be accepted from thewet gas 140 and transferred to a cooling stream or aheat sink 220 for disposal or use elsewhere. Thepassive heat regenerator 200 may include a stack ofplates 230 and the like. Any type of regenerator with good thermal efficiency may be used herein. - The temperature gradient between the
hot heat exchanger 180 and thecold heat exchanger 190 across thepassive heat exchanger 200 of the thermoacoustic resonator may lead to the formation of a number ofacoustic waves 240. Theacoustic waves 240 act as pressure waves that propagate through theacoustic chamber 170 and into thepipe 120. The wavelengths and other characteristics of theacoustic waves 240 may be varied herein. Other types of thermoacoustic resonators and other means for producing theacoustic waves 240 also may be used herein. Other components and other configurations also may be used herein. - As is shown in
FIG. 4 , the pressure front caused by theacoustic waves 240 interacts with thewet gas flow 140 in thepipe 120. The interaction of theacoustic waves 240 may cause a rapid velocity change in thegaseous phase 145 of thewet gas flow 140. The change in the relative velocity between thegaseous phase 145 and theliquid phase 155 of thewet gas flow 140 thus may break up the largeliquid droplets 150 into a number of smallerliquid droplets 250 as thewet gas flow 140 passes through theacoustic waves 240. - Droplet break up may be largely a function of the relative velocity between the
gaseous phase 145 and theliquid phase 155. The potential for droplet break up may be evaluated based upon the Weber number of thewet gas flow 140. Specifically, the Weber number may be calculated in the context of thewet gas flow 140 herein as follows: -
Weber=P g V R 2 d/σ. - In this equation, Pg is the density of the fluid (kg/m3), YR is the relative velocity (m/s), d is the droplet diameter (in), and σ is the surface tension (n/m). Generally described, the Weber number is a non-dimensional measure of the relative importance of the inertia of the fluid as compared to the droplet surface tension. The large
liquid droplets 150 thus may be broken down into the smallerliquid droplets 250 if the Weber number indicates that the kinetic energy of thegaseous phase 145 may overcome the surface tension of thedroplets 150. Other types of droplet evaluation and other types of protocols may be used herein. - The energy of the
acoustic waves 240 may be partially transferred into droplet break up and partially transferred into dissipation in thewet gas flow 140. Dissipation means a deposition of heat into thewet gas flow 140. This heat leads largely to liquid evaporation as opposed to a temperature increase and therefore may be beneficial to overall compressor performance. After passing through theacoustic waves 240, thewet gas flow 140 continues towards thecompressor inlet section 40 with the smallerliquid droplets 250 therein so as to reduce harmful erosion on thecompressor blades 20 and the like. - The wet
gas compression system 100 with thethermoacoustic resonator 160 thus should improve overall lifetime and efficiency of thecompressor 110. Specifically, removal of the largeliquid droplets 150 may improve erosion damage while higher compressor efficiency may be achieved due to evaporation. Moreover, because thethermoacoustic resonator 160 uses no moving parts, thethermoacoustic resonator 160 should have a long lifetime with low maintenance requirements. Further, because thethermoacoustic resonator 160 may use waste heat from thecompressor 110 or elsewhere, thethermoacoustic resonator 160 may not result in parasitic energy loses. Thethermoacoustic resonator 160 also may avoid a pressure drop therethrough such that the main compressor duty may not be increased. - Although the wet
gas compression system 100 described above has been discussed in the context of thethermoacoustic resonator 160 positioned about thepipe 120, thethermoacoustic resonator 160 also may be positioned elsewhere. For example,FIG. 5 andFIG. 6 show the use of thethermoacoustic resonator 160 about a convergent-divergent nozzle 260 or other type of variable cross-section nozzle. As described above, the convergent-divergent nozzle 260, also is known as a de Laval nozzle and the like, may include aconvergent section 270, athroat section 280, and adivergent section 290. The convergent-divergent nozzle 260 may reduce the largeliquid droplets 150 via a supersonic shock at ashock point 300. - In the example of
FIG. 5 , thethermoacoustic resonator 160 may be positioned on an upstream section ofpipe 310. In the example ofFIG. 6 , thethermoacoustic resonator 160 may be positioned on a downstream section ofpipe 320. Thethermoacoustic resonator 160 may be positioned anywhere about or along the convergent-divergent nozzle 260 so as to assist and promote droplet break up in a manner similar to that described above. Multiple thermoacoustic resonators 160 may be used herein. Other type of pipes and other types of nozzles may be used herein. Other components and other configurations also may be used herein. - As an alternative to the
thermoacoustic resonator 160 being in direct fluid communication with thewet gas flow 140 within thepipe 120, thethermoacoustic resonator 160 also may be physically separated from thewet gas flow 140 in thepipe 120. As is shown inFIG. 7 , thethermoacoustic resonator 160 may be connected to thepipe 120 via a movingpiston 330 and the like. Theacoustic waves 240 may drive the movingpiston 330 into contact with thepipe 120 such that the waves continue therein via the mechanical contact. The use of thepiston 330 also allows the use of a different working medium within thethermoacoustic resonator 160. Mediums such as helium, nitrogen, or other gases may be used. The use of an alternative medium may be beneficial from an efficiency and stability point of view, i.e., increased efficiency in the conversion of heat to acoustic energy. Other types of mechanical systems also may be used herein. - It should be apparent that the foregoing relates only to certain embodiments of the present application and the resultant patent. Numerous changes and modifications may be made herein by one of ordinary skill in the art without departing from the general spirit and scope of the invention as defined by the following claims and the equivalents thereof.
Claims (20)
Priority Applications (11)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/295,208 US9382920B2 (en) | 2011-11-14 | 2011-11-14 | Wet gas compression systems with a thermoacoustic resonator |
AU2012339903A AU2012339903A1 (en) | 2011-11-14 | 2012-11-09 | Wet gas compression systems with a thermoacoustic resonator |
MX2014005872A MX2014005872A (en) | 2011-11-14 | 2012-11-09 | Wet gas compression systems with a thermoacoustic resonator. |
EP12806737.8A EP2780599B1 (en) | 2011-11-14 | 2012-11-09 | Wet gas compression systems with a thermoacoustic resonator |
CN201280055785.1A CN103958901B (en) | 2011-11-14 | 2012-11-09 | There is the dampness compressibility of thermoacoustic resonator |
RU2014116877A RU2607576C2 (en) | 2011-11-14 | 2012-11-09 | Wet gas compression system with thermoacoustic resonator |
BR112014011530A BR112014011530A2 (en) | 2011-11-14 | 2012-11-09 | wet gas compression system and method for breaking numerous liquid drops |
PCT/US2012/064490 WO2013074421A1 (en) | 2011-11-14 | 2012-11-09 | Wet gas compression systems with a thermoacoustic resonator |
JP2014541336A JP6159339B2 (en) | 2011-11-14 | 2012-11-09 | Wet gas compression system with thermoacoustic resonator |
KR1020147012783A KR20140093234A (en) | 2011-11-14 | 2012-11-09 | Wet gas compression systems with a thermoacoustic resonator |
NO13725130A NO2856072T3 (en) | 2011-11-14 | 2013-05-21 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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US13/295,208 US9382920B2 (en) | 2011-11-14 | 2011-11-14 | Wet gas compression systems with a thermoacoustic resonator |
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US20130121812A1 true US20130121812A1 (en) | 2013-05-16 |
US9382920B2 US9382920B2 (en) | 2016-07-05 |
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US13/295,208 Active 2033-12-02 US9382920B2 (en) | 2011-11-14 | 2011-11-14 | Wet gas compression systems with a thermoacoustic resonator |
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US (1) | US9382920B2 (en) |
EP (1) | EP2780599B1 (en) |
JP (1) | JP6159339B2 (en) |
KR (1) | KR20140093234A (en) |
CN (1) | CN103958901B (en) |
AU (1) | AU2012339903A1 (en) |
BR (1) | BR112014011530A2 (en) |
MX (1) | MX2014005872A (en) |
NO (1) | NO2856072T3 (en) |
RU (1) | RU2607576C2 (en) |
WO (1) | WO2013074421A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3489526A1 (en) * | 2017-11-22 | 2019-05-29 | Mitsubishi Heavy Industries, Ltd. | Centrifugal compressor and turbocharcher |
US10646804B2 (en) | 2014-12-12 | 2020-05-12 | Nuovo Pignone Tecnologie Srl | System and method for conditioning flow of a wet gas stream |
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US3923415A (en) * | 1974-06-13 | 1975-12-02 | Westinghouse Electric Corp | Steam turbine erosion reduction by ultrasonic energy generation |
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RU2014116877A (en) | 2015-12-27 |
US9382920B2 (en) | 2016-07-05 |
EP2780599B1 (en) | 2018-03-07 |
JP2015504505A (en) | 2015-02-12 |
JP6159339B2 (en) | 2017-07-05 |
NO2856072T3 (en) | 2018-09-29 |
CN103958901A (en) | 2014-07-30 |
MX2014005872A (en) | 2014-06-23 |
AU2012339903A1 (en) | 2014-05-29 |
BR112014011530A2 (en) | 2017-05-16 |
WO2013074421A1 (en) | 2013-05-23 |
CN103958901B (en) | 2016-10-19 |
EP2780599A1 (en) | 2014-09-24 |
RU2607576C2 (en) | 2017-01-10 |
KR20140093234A (en) | 2014-07-25 |
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